US4446785A - Hydraulic clutching and braking system for starting and stopping a power press - Google Patents

Hydraulic clutching and braking system for starting and stopping a power press Download PDF

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Publication number
US4446785A
US4446785A US06/305,839 US30583981A US4446785A US 4446785 A US4446785 A US 4446785A US 30583981 A US30583981 A US 30583981A US 4446785 A US4446785 A US 4446785A
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US
United States
Prior art keywords
brake
clutch
press
friction pads
drive shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US06/305,839
Other languages
English (en)
Inventor
Carl E. Tack, Jr.
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wabash Alloys Inc
Danly Komatsu LP
Avondale Industries Inc
Original Assignee
Danly Machine Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Danly Machine Corp filed Critical Danly Machine Corp
Priority to US06/305,839 priority Critical patent/US4446785A/en
Assigned to DANLY MACHINE CORPORATION, A CORP. OF DE. reassignment DANLY MACHINE CORPORATION, A CORP. OF DE. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: TACK, CARL E. JR.
Priority to CA000410599A priority patent/CA1195175A/en
Priority to AU88330/82A priority patent/AU8833082A/en
Priority to KR8204186A priority patent/KR880000612B1/ko
Priority to EP82305042A priority patent/EP0076111B1/de
Priority to DE8282305042T priority patent/DE3276933D1/de
Priority to BR8205641A priority patent/BR8205641A/pt
Priority to ES516011A priority patent/ES516011A0/es
Priority to JP57169462A priority patent/JPS5868499A/ja
Priority to AR290797A priority patent/AR229057A1/es
Publication of US4446785A publication Critical patent/US4446785A/en
Application granted granted Critical
Assigned to FIRST NATIONAL BANK OF BOSTON THE reassignment FIRST NATIONAL BANK OF BOSTON THE SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CONNELL LIMITED PARTNERSHIP, A DE. LIMITED PARTNERSHIP
Assigned to AVONDALE INDUSTRIES, INC. reassignment AVONDALE INDUSTRIES, INC. MERGER (SEE DOCUMENT FOR DETAILS). Assignors: LURIA BROTHERS & COMPANY, INC., ORTNER FREIGHT CAR COMPANY, WABASH ALLOYS, INC., YUBA HEAT TRANSFER CORP.
Assigned to WABASH ALLOYS, INC. reassignment WABASH ALLOYS, INC. MERGER (SEE DOCUMENT FOR DETAILS). Assignors: DANLY MACHINE CORPORATION
Assigned to FIRST NATIONAL BANK OF BOSTON, THE reassignment FIRST NATIONAL BANK OF BOSTON, THE SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). APRIL 30, 1990 Assignors: CONNELL LIMITED PARTNERSHIP
Assigned to CONNELL LIMITED PARTNERSHIP reassignment CONNELL LIMITED PARTNERSHIP PARTIAL RELEASE OF SECURITY INTEREST DATED ON APRIL 30, 1990 Assignors: FIRST NATIONAL BANK OF BOSTON, THE
Assigned to FIRST NATIONAL BANK OF BOSTON, THE reassignment FIRST NATIONAL BANK OF BOSTON, THE SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DANLY-KOMATSU L.P., A DE LIMITED PARTNERSHIP
Assigned to DANLY-KOMATSU L.P. A DE LIMITED PARTNERSHIP reassignment DANLY-KOMATSU L.P. A DE LIMITED PARTNERSHIP ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: CONNELL LIMITED PARTNERSHIP, A DE LIMITED PARTNERSHIP
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/10—Brakes specially adapted for presses
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/12—Clutches specially adapted for presses
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/14—Control arrangements for mechanically-driven presses
    • B30B15/142—Control arrangements for mechanically-driven presses controlling the brake or the clutch

Definitions

  • the present invention relates generally to power presses and, more particularly, to an improved clutching and braking system for starting and stopping a power press.
  • Power presses are generally started and stopped by means of pneumatically operated clutch and brake mechanisms, although mechanical and eddy current clutches and brakes are also used to some extent.
  • the press is started by pneumatically disengaging the brake and pneumatically actuating the clutch to engage the press drive, after which the pneumatic pressure continues to increase to build up the desired full clutch torque.
  • the press drive is accelerated at an extremely rapid rate.
  • the pneumatic pressure on both the brake and the clutch must be dissipated, after which the brake is applied by means of mechanical spring pressure. Dissipation of the pneumatic pressure sufficiently to engage the brake and disengage the clutch takes a long time, relative to the duration of one press cycle. In order to stop the press within a reasonable segment of a press cycle, therefore, the brake is normally applied with an extremely high force which stops the press rather abruptly after the clutch has been disengaged.
  • the abrupt transitions produced by the pneumatic system described above can disrupt the automation system and cause damage to the workpieces or the automation equipment.
  • the automation system must be programmed to provide excessive clearances between the various controlled mechanisms, which reduces the productivity of the press system.
  • a primary object of the present invention to provide an improved system for starting and stopping a power press quickly and yet smoothly so as to avoid abrupt movements of the type that can disrupt the automation system.
  • a related object of the invention is to provide such a starting and stopping system which permits rapid response to signals commanding the press to start or stop, but which starts and stops the press in a "soft" manner without excessive rates of acceleration and deceleration.
  • Another important object of this invention is to provide such an improved starting and stopping system which permits increases in the productivity of an automated press system having automatically controlled workpiece handling mechanisms.
  • a further object of this invention is to provide an improved fast-acting but "soft" clutching and braking system for a power press.
  • Still another object of the invention is to provide an improved clutching and braking system which permits the brake to be applied at the same time that the clutch is being disengaged, thereby minimizing the stopping time and motion.
  • a system for starting and stopping a power press having a slide mechanism mounted for reciprocating movement, a press drive for cycling the slide mechanism, a clutch for connecting and disconnecting a press drive and the slide mechanism, and a brake for braking the press drive shaft
  • the system comprising means for starting the press by hydraulically disengaging the brake and hydraulically engaging the clutch at a predetermined intermediate torque level which is less than the full clutch torque level, and then maintaining the clutch at the intermediate torque level until the press drive shaft has attained substantially full speed, after which the clutch torque is increased to the full clutch torque level; and means for stopping the press by hydraulically disengaging the clutch and engaging the brake at a predetermined intermediate torque level which is less than the full brake torque, and then maintaining the brake at the intermediate torque level until the press drive shaft has substantially stopped, after which the brake torque is increased to the full brake torque level.
  • FIGS. 1a and 1b are response curves for a typical prior art pneumatic clutching and braking system for a power press
  • FIGS. 2a and 2b are response curves for a hydraulic clutching and braking system embodying the invention and using the brake and clutch mechanisms illustrated in FIGS. 1-4.
  • FIG. 3 is an end elevation view of a hydraulic brake for use in a press starting and stopping system embodying the invention, with a fragment thereof broken away to show the underlying structure;
  • FIG. 4 is a section taken generally along line 4--4 in FIG. 3;
  • FIG. 5 is an end elevation of a hydraulic clutch for use in a press starting and stopping system embodying the invention, with fragments thereof broken away to show the underlying structure;
  • FIG. 6 is a section taken generally along line 6--6 in FIG. 5.
  • FIGS. 1a and 1b illustrate typical response curves for a pneumatic clutching and braking system that has been used in power presses for a number of years.
  • the brake in such a system is usually engaged by mechanical springs and disengaged by pneumatic pressure acting against the spring pressure, whereas the clutch is engaged by pneumatic pressure and disengaged by merely exhausting the pneumatic pressure.
  • a solenoid is energized at time t1 to actuate a valve that initiates the application of pneumatic pressure to both the brake and the clutch at time t2, following a short "electrical delay" for operation of the solenoid valve.
  • the pneumatic pressure then begins to build up, and at time t3 the clutch engages, albeit at a torque level well below the full clutch torque level. Following initial engagement of the clutch at time t3, the clutch torque continues to increase until it reaches its maximum level at time t5. While the clutch torque is increasing, the press drive shaft accelerates at an increasingly rapid rate, particularly when the clutch approaches its full torque level. For example, in a typical power press using such a pneumatic clutching and braking system, the press drive shaft is accelerated to full speed in less than 2 seconds, producing acceleration forces in excess of 3.3 "g"'s.
  • the brake disengages at time t4.
  • the brake remains disengaged until a solenoid is de-energized to stop the press, at time t6 in FIGS. 1a and 1b.
  • This solenoid actuates a valve that exhausts the pneumatic pressure from both the clutch and the brake, but at a slower rate from the brake than from the clutch because the brake cannot be engaged until the clutch torque has been reduced to a certain level.
  • the pneumatic pressure on both the brake and the clutch begins to diminish at the different rates.
  • the brake is finally engaged at time t8, just slightly before the pneumatic pressure on the clutch drops sufficiently to disengage the clutch at time t9. Following engagement of the brake at time t8, the brake torque increases rapidly with a correspondingly rapid deceleration of the press drive shaft.
  • FIGS. 2a and 2b illustrate the response curves for a hydraulic clutching and braking system according to the present invention.
  • Secific clutch and brake mechanisms for use in this hydraulic system will be described in detail below, but it will be helpful to first understand the operating characteristics of the system as illustrated in FIGS. 2a and 2b.
  • a solenoid is energized at time t10 to actuate a valve that removes hydraulic pressure from the brake and applies hydraulic pressure to the clutch.
  • this system immediately disengages the brake and engages the clutch at time t11.
  • the hydraulic system reacts almost instantaneously--much faster than a pneumatic system.
  • the brake torque immediately drops to zero at time t11, and the clutch torque immediately increases to an intermediate torque level determined by one of two sources of hydraulic pressure for the clutch.
  • the intermediate torque level is typically about 10% of full clutch torque.
  • the clutch is maintained at this intermediate torque level for a preselected time interval, extending from time t11 to time t12 in FIG. 2b, which is sufficient to bring the press drive shaft up to full speed.
  • the hydraulic pressure on the clutch is increased to immediately raise the clutch torque to its full-on level, which is determined by the source of hydraulic pressure for the clutch.
  • a tachometer can be used to monitor the actual speed of the press drive shaft and detect when it reaches full speed.
  • the tachometer output can be used to produce a signal which automatically connects the full-on pressure source to the clutch as soon as the drive shaft reaches full speed.
  • the drive shaft is accelerated at a much more constant rate than in the pneumatic system described above. More specifically, the acceleration of the drive shaft begins more quickly, and initially at a faster rate, because of the immediate response of the hydraulic system. Later on in the startup interval (t11 to t12), the acceleration produced by the hydraulic system is slower than that produced by the pneumatic system because the hydraulic system brings the drive shaft up to speed at a relatively constant rate of acceleration, avoiding the extremely high acceleration forces produced by the pneumatic system toward the end of the startup interval.
  • the hydraulic system provides a "soft" startup without any abrupt transitions or high acceleration rates which can upset the automation system and the workpiece handling mechanisms controlled thereby.
  • the maximum acceleration force during startup with the system of FIGS. 2a and 2b is only bout one "g".
  • the clutch torque After the clutch torque has been increased to its full-on level at time t12, it is maintained at this level until it is desired to stop the press. Stopping is initiated by de-energizing a solenoid at time t13 to actuate a valve that applies hydraulic pressure to the brake and removes hydraulic pressure from the clutch. Following another brief “electrical delay” from time t13 to time t14, this immediately disengages the clutch and engages the brake (at time t14). The brake torque is initially limited, however, to an intermediate torque level, e.g., 40% in the example of FIG. 2a, until the press drive shaft has been substantially stopped at time t15.
  • an intermediate torque level e.g. 40% in the example of FIG. 2a
  • Stopping the drive shaft with this intermediate level of brake torque provides a "soft" stop, i.e., the drive shaft is decelerated at a relatively slot and constant rate to avoid abrupt transitions of the type produced by the pneumatic system described above. Consequently, the hydraulic braking action does not disrupt the automation system or the workpiece handling mechanisms controlled thereby.
  • the full hydraulic pressure is applied to the brake to produce full brake torque.
  • the brake is then maintained at this full torque level until it is desired to start the press again.
  • the two different torque levels for the hydraulic brake are determined by two sources of hydraulic pressure for the brake.
  • the brake is connected to the first source, which sets the intermediate torque level, from time t14 to time t15, and then is switched to the second source, which sets the full-on torque level.
  • FIGS. 3 and 4 there is shown a hydraulically operated brake for applying a braking torque to a press drive shaft 10.
  • a brake disc 11 is affixed to a hub 12 on the end of the shaft 10, and a plurality of brake pads 13 are carried by the disc 11 and arranged in a symmetrical array around the circumference of the disc.
  • a movable gripper ring 14 is advanced into engagement with one side of the brake pads 13 to press the pads against a stationary gripper ring 15 fastened to the press frame 16.
  • a multiplicity of radial ribs 15a are formed on the outside of the ring 15.
  • the movable gripper ring 14 is advanced into its engaged position by means of hydraulic pressure supplied through a line 20 to a piston 21 slidably mounted in a primary cylinder plate 22.
  • the hydraulic pressure moves the piston 21 to the left, as viewed in FIG. 4, thereby advancing a pressure plate 23 which is rigidly connected to the movable gripper ring 14 by means of a plurality of bolts 24 and spacers 25.
  • the hydraulic pressure is simply removed from the line 20.
  • two circular arrays of compressed coil springs 30 and 31 are mounted in recesses formed in the surface of the primary cylinder plate 22 and mating recesses formed in the adjacent surface of a plate 32 which are rigidly fastened to the press frame by a plurality of bolts 33.
  • the pressure of these springs 30 and 31 urges the cylinder plate 22 to the left as viewed in FIG. 4, but such movement of the cylinder plate is prevented during normal operation of the brake by an over-riding hydraulic pressure. More specifically, hydraulic pressure is applied through a line 32 to an annular cylinder 33 formed by a secondary cylinder plate 34 and containing an annular piston 35.
  • the two cylinder plates 22 and 34 are connected by a plurality of machine screws 36 passing through corresponding spacers 37, which in turn pass through the fixed plate 32.
  • the two cylinder plates 22 and 34 are linked together in a rigid assembly which can be moved back and forth relative to the fixed plate 32 which is disposed between the two cylinder plates to provide a stationary support for one end of the springs 30 and 31.
  • the hydraulic pressure from the line 32 will drop off, because the line 32 is connected to the same pressure source as the primary actuator line 20.
  • the springs 30 and 31 move the two cylinder plates 22 and 34 to the left (as viewed in FIG. 4) thereby advancing the movable gripper ring 14 into engagement with the friction pads 13 to apply the brake. Consequently, the brake fails in a safe mode, automatically braking the press drive shaft in the event of a malfunction in the hydraulic system.
  • FIGS. 5 and 6 A hydraulically operated clutch, for use in conjunction with the hydraulic brake of FIGS. 3 and 4, is shown in FIGS. 5 and 6.
  • the clutch is used to connect and disconnect the press drive shaft 10 and a flywheel 40 through a clutch disc 41 affixed to a hub 42 on the drive shaft.
  • a plurality of friction pads 43 are carried by the disc 41 in a symmetrical array around the circumference of the disc.
  • a movable gripper ring 44 is advanced into engagement with one side of the friction pads 43 to press the pads against a stationary gripper ring 45 fastened to the flywheel 40.
  • a multiplicity of fins 45a are formed on the outside of the ring 45.
  • the movable gripper ring 44 is advanced into its engaged position by means of hydraulic pressure supplied through a line 46 and a rotary coupling 47 to a piston 48 slidably mounted in a cylinder plate 49.
  • the hydraulic pressure moves the piston 48 to the left, as viewed in FIG. 6, thereby advancing a pressure plate 50 which is rigidly connected to the movable gripper ring 44 by means of a spacer ring 51.
  • the hydraulic pressure is simply removed from the line 46.
  • this invention provides an improved clutch and brake system for starting and stopping a power press quickly and yet smoothly so as to avoid abrupt movements of the type that can disrupt automation systems.
  • This system permits rapid response to signals commanding the press to start or stop, while at the same time starting and stopping the press in a "soft" manner without excessive rates of acceleration and deceleration.
  • the brake can be applied at the same time that the clutch is being disengaged, thereby minimizing the stopping time and motion.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Presses (AREA)
  • Braking Arrangements (AREA)
US06/305,839 1981-09-28 1981-09-28 Hydraulic clutching and braking system for starting and stopping a power press Expired - Fee Related US4446785A (en)

Priority Applications (10)

Application Number Priority Date Filing Date Title
US06/305,839 US4446785A (en) 1981-09-28 1981-09-28 Hydraulic clutching and braking system for starting and stopping a power press
CA000410599A CA1195175A (en) 1981-09-28 1982-09-01 Hydraulic clutching and braking system for starting and stopping a power press
AU88330/82A AU8833082A (en) 1981-09-28 1982-09-13 Hydraulic clutch/brake system for start/stop of press
KR8204186A KR880000612B1 (ko) 1981-09-28 1982-09-15 동력프레스의 기동 및 정지용 유압클러치 및 브레이크 시스템
EP82305042A EP0076111B1 (de) 1981-09-28 1982-09-24 Kupplungs- und Bremssystem zum Starten und Stoppen einer Leistungspresse
DE8282305042T DE3276933D1 (en) 1981-09-28 1982-09-24 Clutching and braking system for starting and stopping a power press
BR8205641A BR8205641A (pt) 1981-09-28 1982-09-27 Processo e aparelho para dar a partida e parar uma prensa mecanica
AR290797A AR229057A1 (es) 1981-09-28 1982-09-28 Aparato para hacer arrancar y detener una prensa mecanica
ES516011A ES516011A0 (es) 1981-09-28 1982-09-28 Procedimiento para poner en marcha y detener una prensa mecanica.
JP57169462A JPS5868499A (ja) 1981-09-28 1982-09-28 動力プレスにおけるクラツチ機構及びブレ−キ機構とその駆動方法

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US06/305,839 US4446785A (en) 1981-09-28 1981-09-28 Hydraulic clutching and braking system for starting and stopping a power press

Publications (1)

Publication Number Publication Date
US4446785A true US4446785A (en) 1984-05-08

Family

ID=23182586

Family Applications (1)

Application Number Title Priority Date Filing Date
US06/305,839 Expired - Fee Related US4446785A (en) 1981-09-28 1981-09-28 Hydraulic clutching and braking system for starting and stopping a power press

Country Status (10)

Country Link
US (1) US4446785A (de)
EP (1) EP0076111B1 (de)
JP (1) JPS5868499A (de)
KR (1) KR880000612B1 (de)
AR (1) AR229057A1 (de)
AU (1) AU8833082A (de)
BR (1) BR8205641A (de)
CA (1) CA1195175A (de)
DE (1) DE3276933D1 (de)
ES (1) ES516011A0 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6006660A (en) * 1998-08-12 1999-12-28 The Minster Machine Company Segmented drive disk for a mechanical press

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2102289B1 (es) * 1992-12-02 1998-01-16 Coop Goizper S Freno-embrague neumatico mejorado.
JP2010158718A (ja) * 2008-12-08 2010-07-22 Sumitomo Heavy Industries Techno-Fort Co Ltd 湿式クラッチブレーキの油圧制御装置
JP5091928B2 (ja) * 2009-08-10 2012-12-05 住友重機械テクノフォート株式会社 機械プレスのクラッチブレーキ制御装置
DE202014007305U1 (de) 2014-09-08 2015-01-09 Siempelkamp Maschinen- Und Anlagenbau Gmbh Spindelpresse

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2436968A (en) * 1945-07-31 1948-03-02 Cleveland Punch & Shear Works Combined clutch and brake
US2577641A (en) * 1950-05-05 1951-12-04 Minster Machine Co Multiple drive press with multiple clutch
US2838150A (en) * 1954-10-29 1958-06-10 Ind Clutch Corp Interconnected clutch and brake mechanism
US3580371A (en) * 1969-10-16 1971-05-25 King Of Prussia Research & Dev Self-synchronizing clutch
GB1491203A (en) * 1974-10-21 1977-11-09 Volvo Ab Devices for limiting torsional shocks

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE717082C (de) * 1939-07-28 1942-02-05 Miag Muehlenbau Und Ind Ag Hydraulisch gesteuerte Bremsekupplung
US2905290A (en) * 1954-05-25 1959-09-22 Niagara Machine & Tool Works Clutch brake sequence control for power presses and the like
GB804482A (en) * 1955-12-05 1958-11-19 Eumuco Ag Fur Maschb An improved torque transmission device for use in presses and other workshop machinery
US3000478A (en) * 1959-07-16 1961-09-19 Ferracute Machine Company Clutch-brake mechanism
US3224538A (en) * 1963-06-20 1965-12-21 William E Ward Clutch unit for power press
DE1502319A1 (de) * 1965-01-05 1969-04-10 Schuler Gmbh L Pressenkupplung
US3371759A (en) * 1967-02-07 1968-03-05 Bliss E W Co Clutch control for mechanical devices
DE2412195A1 (de) * 1974-03-14 1975-09-18 Ortlinghaus Werke Gmbh Hydraulisch schaltbare kupplungsbremsvorrichtung
JPS5434952A (en) * 1977-08-23 1979-03-14 Redei Kk Shoes making method

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2436968A (en) * 1945-07-31 1948-03-02 Cleveland Punch & Shear Works Combined clutch and brake
US2577641A (en) * 1950-05-05 1951-12-04 Minster Machine Co Multiple drive press with multiple clutch
US2838150A (en) * 1954-10-29 1958-06-10 Ind Clutch Corp Interconnected clutch and brake mechanism
US3580371A (en) * 1969-10-16 1971-05-25 King Of Prussia Research & Dev Self-synchronizing clutch
GB1491203A (en) * 1974-10-21 1977-11-09 Volvo Ab Devices for limiting torsional shocks

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6006660A (en) * 1998-08-12 1999-12-28 The Minster Machine Company Segmented drive disk for a mechanical press

Also Published As

Publication number Publication date
JPS5868499A (ja) 1983-04-23
EP0076111A2 (de) 1983-04-06
CA1195175A (en) 1985-10-15
DE3276933D1 (en) 1987-09-17
BR8205641A (pt) 1983-08-30
ES8403380A1 (es) 1984-03-16
AR229057A1 (es) 1983-05-31
EP0076111A3 (en) 1984-06-06
ES516011A0 (es) 1984-03-16
KR880000612B1 (ko) 1988-04-18
AU8833082A (en) 1983-04-14
KR840001477A (ko) 1984-05-07
EP0076111B1 (de) 1987-08-12

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Owner name: DANLY MACHINE CORPORATION, 2100 SOUTH LARAMIE AVE.

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